EP4403786A1 - Gaslager für zentrifugalverdichter, zentrifugalverdichter und kühlsystem - Google Patents

Gaslager für zentrifugalverdichter, zentrifugalverdichter und kühlsystem Download PDF

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Publication number
EP4403786A1
EP4403786A1 EP24152146.7A EP24152146A EP4403786A1 EP 4403786 A1 EP4403786 A1 EP 4403786A1 EP 24152146 A EP24152146 A EP 24152146A EP 4403786 A1 EP4403786 A1 EP 4403786A1
Authority
EP
European Patent Office
Prior art keywords
motor shaft
centrifugal compressor
gas bearing
housing
electromagnetic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP24152146.7A
Other languages
English (en)
French (fr)
Inventor
Wei Zhang
Jiedong LI
Jun Cao
Caiyan JIN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP4403786A1 publication Critical patent/EP4403786A1/de
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/024—Sliding-contact bearings for exclusively rotary movement for radial load only with flexible leaves to create hydrodynamic wedge, e.g. radial foil bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0474—Active magnetic bearings for rotary movement
    • F16C32/048—Active magnetic bearings for rotary movement with active support of two degrees of freedom, e.g. radial magnetic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/09—Structural association with bearings with magnetic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2362/00—Apparatus for lighting or heating
    • F16C2362/52—Compressors of refrigerators, e.g. air-conditioners

Definitions

  • the present invention relates to the field of refrigeration technology, in particular to a gas bearing for a centrifugal compressor, and further to a centrifugal compressor configured with the gas bearing, as well as a refrigeration system equipped with the centrifugal compressor.
  • oil-free lubrication technology is gradually adopted to replace the original oil lubrication for centrifugal compressors, thereby saving the trouble of managing lubricating oil systems, such as oil circuit maintenance, oil return management, and oil circuit system maintenance.
  • oil-free lubrication also represents higher compressor operating efficiency and higher refrigeration system operating efficiency, lower vibration and noise, stable operation, significantly reduced costs, cleaner energy, and better user experience.
  • Gas bearing is a low-cost and highly promising way and means to solve the problem of oil-free lubrication for centrifugal compressors.
  • Gas bearing uses gas as the lubricating medium. After the rotating speed reaches a certain value (i.e., the lift-off speed), a stable gas film is formed between the foil and the rotor, thereby achieving the effect of the bearing. Therefore, it has the advantages such as high speed, low friction, oil-free lubrication, and a wide range of applicable temperatures, thus having broad application prospects in high-speed rotating machinery, such as centrifugal compressors used in the refrigeration field.
  • the centrifugal compressor supported by gas bearing consists of housing, volute, impeller, radial and thrust gas bearing, high-speed motor, and other components.
  • the high-speed motor is supported by gas bearings at the left and right ends, resulting in low rotational resistance and high rotational speed.
  • the dry friction between the foil of the gas bearing and the motor shaft affects the stability of the bearing, thus requiring a high level of friction-resistant coating on the foil. It is also an important factor that affects the stable operation of the foil bearing and limits its widespread application.
  • a gas bearing for a centrifugal compressor which effectively solves the above problems and problems in other aspects existing in the prior art.
  • the centrifugal compressor comprises a housing and a motor shaft located within the housing, the gas bearing comprising:
  • the top of the bearing housing may be provided with a groove for accommodating the electromagnetic stator.
  • the groove may pass through the front and rear end faces of the bearing housing in the axial direction of the motor shaft; or the groove is located in the middle of the top of the bearing housing.
  • the electromagnetic stator may be located at an end side of the top of the bearing housing.
  • the motor shaft may be provided with a sleeve, and the electromagnetic rotor is fixed on the sleeve in a nested manner.
  • the bearing housing and/or the sleeve may be made of steel.
  • the electromagnetic stator and/or the electromagnetic rotor may be made of silicon steel sheets.
  • the length of the electromagnetic stator and that of the electromagnetic rotor may be the same in the axial direction of the motor shaft.
  • centrifugal compressor configured with gas bearing as described in the first aspect above.
  • a centrifugal compressor comprising the gas bearing of the first aspect.
  • a refrigeration system equipped with the centrifugal compressor as described in the second aspect.
  • a refrigeration system comprising the centrifugal compressor as described in the second aspect.
  • the gas bearing for a centrifugal compressor adopts an electromagnetic structure design, which, by providing a vertically upward electromagnetic force to counteract part or all of the gravity of the motor shaft itself, provides a certain amount of electromagnetic force to the motor shaft during the start-up/shut-down stage of the centrifugal compressor, so as to reduce or avoid the dry friction between the motor shaft and the foil, lower the load of the gas bearing, reduce the wear during the start-up/shut-down process of the bearing, and prolong the service life of the gas bearing, thus providing system stability and expanding the application range of centrifugal compressors with gas bearing or foil bearing.
  • any technical features or solutions in the embodiments are one or several of multiple optional technical features or technical solutions.
  • FIG. 1 schematically illustrates the structure of a first embodiment of a gas bearing for a centrifugal compressor according to the present invention in general.
  • the centrifugal compressor comprises a housing (not shown) and a motor shaft 110 located within the housing.
  • the motor shaft 110 is supported by a gas bearing during rotation, where the end of the motor shaft 110 extends from the motor cavity and is mounted with an impeller (not shown).
  • the motor cavity can be a part of the housing or a fixed component independent of the housing.
  • the gas bearing 120 is composed of a bearing housing 121, an electromagnetic stator 122, an electromagnetic rotor 123, a foil 124, and other components.
  • the bearing housing 121 is sleeved on the outer side of the motor shaft 110 and fixed on the housing of the centrifugal compressor.
  • the electromagnetic stator 122 is fixed in the middle of the top of the bearing housing 121 or near the top of the bearing housing 121, and is wound with a coil 125 that can be powered.
  • the electromagnetic stator 122 can be composed of iron core laminations and coil wound on the laminations.
  • the electromagnetic rotor 123 is fixed on the outer surface of the motor shaft 110 and arranged circumferentially around the motor shaft 110.
  • the electromagnetic rotor 123 can be composed of laminations.
  • the motor shaft 110 can overcome part or all of its own gravity and levitate relative to the foil 124, thereby reducing or avoiding the dry friction between the motor shaft 110 and the foil 124 during the start-up/shutdown stage of the centrifugal compressor, and further improving the system stability of the centrifugal compressor and expanding the application range of centrifugal compressors with gas bearing.
  • "Levitate” here refers to the state in which the motor shaft maintains a relatively constant interval relative to the gas bearing.
  • the foil 124 is located between the bearing housing 121 and the motor shaft 110, and is fixed on the bearing housing 121.
  • the foil 124 is composed of one or more layers of corrugated bump foil and top foil, with a good flexible surface and a friction-resistant coating attached to the top foil on the side near the rotor.
  • the foil 124 by means of the relative motion between the motor shaft 110 and the surface of the gas bearing, allows the motor shaft 110 to introduce gas with a certain viscosity into the limited space between the motor shaft and the top foil for compression, forming a lubricating gas film with a certain pressure, thereby keeping the motor shaft levitated.
  • the coil can be powered during the start-up/shut-down stage of the centrifugal compressor or when the motor shaft of the centrifugal compressor rotates at a speed lower than the lift-off speed.
  • the vertically upward electromagnetic force formed by the electromagnetic stator and the electromagnetic rotor counteracts or at least partially counteracts the gravity of the motor shaft, thus allowing the motor shaft to overcome its own gravity to be levitated.
  • the stable gas film formed by the gas bearing enables the motor shaft to be kept levitated without the need to continue powering the coil.
  • the electromagnetic stator can still be continuously energized to provide electromagnetic force, so as to expand the overall load capacity of the gas bearing and improve the application range of centrifugal compressors with gas bearing.
  • the motor shaft 110 is provided with a sleeve 111, which can be tightly fitted to the motor shaft 110, and the electromagnetic rotor 123 is fixed in the sleeve 111, playing a role in compressing and fixing the laminations.
  • the length of the electromagnetic stator 122 and that of the electromagnetic rotor 123 are the same in the axial direction of the motor shaft 110, as shown in FIG. 1 .
  • the top of the bearing housing 121 is provided with a groove for accommodating the electromagnetic stator 122.
  • the groove can pass through the front and rear end faces of the bearing housing 121 in the axial direction of the motor shaft 110.
  • the shape and size of the groove are not limited to this.
  • a motor shaft 210, a bearing housing 221, a bearing sleeve 211, an electromagnetic stator 222, a coil 225, an electromagnetic rotor 223, and a foil 224 etc. in the gas bearing 220 can refer to the previous embodiment, which will not be repeated here.
  • the motor shaft 210 or the rotor has a relatively small volume and light weight, so the groove can be arranged in the middle of the top of the bearing housing 221 to accommodate the electromagnetic stator 222.
  • a motor shaft 310, a bearing housing 321, a bearing sleeve 311, an electromagnetic stator 322, a coil 325, an electromagnetic rotor 323, and a foil 324 etc. in the gas bearing 320 can refer to the previous embodiments, which will not be repeated here.
  • the electromagnetic stator 322 is located at an end side of the top of the bearing housing 321.
  • the bearing housing 121 and/or the sleeve 111 are made of steel.
  • the electromagnetic stator 122 and/or the electromagnetic rotor 123 are made of laminated silicon steel sheets, so as to effectively suppress eddy currents generated on the surface of the motor shaft 110.
  • the size, shape, and position of the silicon steel sheets can be adjusted according to actual production or design needs, which are not limited here.
  • the present invention does not provide detailed description for the design of the foil. Therefore, the gas bearing of the present invention can be applied to a wide range of foil forms, and to different arrangements in the circumferential and axial directions.
  • the present invention also provides a centrifugal compressor configured with the gas bearing according to the various embodiments.
  • the centrifugal compressor can include a first stage or a second stage of two-stage compression with a back-to-back design: a low-pressure stage compression composed of a first impeller assembly, and a high-pressure stage compression composed of a second impeller assembly, wherein the second impeller assembly (i.e., the impeller of the second stage) is generally smaller than the first impeller assembly (i.e., the impeller of the first stage), where the inlet of the impeller of the second stage is the outlet of the impeller of the first stage.
  • the centrifugal compressor can also include a first stage or a second stage where two stages are arranged in parallel with a back-to-back design, wherein the impeller sizes of the two stages are the same, that is, the inlet and outlet arrangements are the same.
  • the first impeller assembly is located at a first end of the motor shaft, and the second impeller assembly is located at a second end of the motor shaft.
  • the centrifugal compressor there can be two sets of radial gas bearings, i.e., a first set of gas bearings and a second set of gas bearings, wherein the first set of gas bearings can be arranged between the motor cavity and the first impeller assembly, and the second set of gas bearings can be arranged between the motor cavity and the second impeller assembly.
  • the thrust disk can be located on the first impeller assembly side or the second impeller assembly side.
  • the gas bearing is not limited to being applied to the two-stage compressor with a back-to-back design.
  • a compressor with one to multiple impellers arranged in series can also use the aforementioned gas bearing.
  • the present invention further provides a refrigeration system equipped with the aforementioned centrifugal compressor.
  • the refrigeration system may include a cooling tower, a water chilling unit, and a pumping device etc. connected through pipelines, wherein the water chilling unit is composed of a centrifugal compressor, a condenser, a throttling device, an evaporator, and other components.
  • centrifugal compressors equipped with the aforementioned gas bearing can effectively improve system stability. Therefore, it is highly recommended to apply the aforementioned centrifugal compressors to various refrigeration systems.
  • the gas bearing for a centrifugal compressor adopts an electromagnetic structure design, which, by providing a vertically upward electromagnetic force to counteract part or all of the gravity of the motor shaft itself, allows the motor shaft to levitate during the start-up/shut-off stage of the centrifugal compressor, thus reducing or avoiding the dry friction between the motor shaft and the bearing housing, so as to improve system stability and expand the application range of centrifugal compressors with the gas bearing.
  • fixed connections can be understood as fixed connections in a detachable manner (such as connections using bolts or screws), or as fixed connections in a non-detachable manner (such as through riveting, welding).
  • fixed connections to each other can also be replaced by integrated structures (such as those manufactured into one piece using casting technology), except that when it is evidently impossible to use the integration process.
  • any component provided by the present invention can be either assembled from multiple individual components or manufactured as a separate component using an integration process.
  • orientations or positional relationships indicated by the above terms are based on the orientations or positional relationships shown in the drawings. These terms are used merely for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device, mechanism, component or element referred to must have a specific orientation, be constructed and operated in a specific orientation, so they cannot be understood as forming limitations on the scope of protection of the present invention.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Power Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP24152146.7A 2023-01-18 2024-01-16 Gaslager für zentrifugalverdichter, zentrifugalverdichter und kühlsystem Pending EP4403786A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202310074764.4A CN118361413A (zh) 2023-01-18 2023-01-18 用于离心压缩机的气浮轴承、离心压缩机以及制冷系统

Publications (1)

Publication Number Publication Date
EP4403786A1 true EP4403786A1 (de) 2024-07-24

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP24152146.7A Pending EP4403786A1 (de) 2023-01-18 2024-01-16 Gaslager für zentrifugalverdichter, zentrifugalverdichter und kühlsystem

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US (1) US20240240645A1 (de)
EP (1) EP4403786A1 (de)
CN (1) CN118361413A (de)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6965181B1 (en) * 1997-09-15 2005-11-15 Mohawk Innovative Technology, Inc. Hybrid foil-magnetic bearing with improved load sharing
CN104852509A (zh) * 2015-06-11 2015-08-19 韩景 磁悬浮式相对转动发电机
CN105099108A (zh) * 2014-05-22 2015-11-25 华为技术有限公司 风扇电机及风扇
US20190120292A1 (en) * 2016-03-04 2019-04-25 Technologies' Xanadu Of Resonatory-Solar-Systemed Co., Ltd. Electromagnetically enabled active dynamic pressure gas bearing
US20210062715A1 (en) * 2018-01-12 2021-03-04 Technologies' Xanadu Of Resonatory-Solar-Systemed Co., Ltd. Rotor system and control method thereof, as well as gas turbine generator set and control method thereof
US20210404720A1 (en) * 2020-06-24 2021-12-30 Carrier Corporation Foil bearing lubrication

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6965181B1 (en) * 1997-09-15 2005-11-15 Mohawk Innovative Technology, Inc. Hybrid foil-magnetic bearing with improved load sharing
CN105099108A (zh) * 2014-05-22 2015-11-25 华为技术有限公司 风扇电机及风扇
CN104852509A (zh) * 2015-06-11 2015-08-19 韩景 磁悬浮式相对转动发电机
US20190120292A1 (en) * 2016-03-04 2019-04-25 Technologies' Xanadu Of Resonatory-Solar-Systemed Co., Ltd. Electromagnetically enabled active dynamic pressure gas bearing
US20210062715A1 (en) * 2018-01-12 2021-03-04 Technologies' Xanadu Of Resonatory-Solar-Systemed Co., Ltd. Rotor system and control method thereof, as well as gas turbine generator set and control method thereof
US20210404720A1 (en) * 2020-06-24 2021-12-30 Carrier Corporation Foil bearing lubrication

Also Published As

Publication number Publication date
US20240240645A1 (en) 2024-07-18
CN118361413A (zh) 2024-07-19

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